Pumps and motors

ABSTRACT

A fluid pressure orbiting piston oscillating cylinder machine for use as a fluid pump or motor having a drive or driven power shaft rotatably mounted in a housing and having an eccentric and crank mechanism supporting a spider for orbiting movement. The spider has a plurality of radial arms each having fixed on the radial outer end a spherical piston fitting in a cylindrical cylinder. Each piston is coaxially aligned with the radius of its spider arm. The cylinder has a transverse cylindrical base in bearing engagement with a fixed internal cylindrical bearing surface coaxial with the shaft. A manifold in the housing is connected by ports in the internal cylindrical bearing which cooperate with ports in the cylinder base so that during rotation of the power shaft the pistons orbit in a circular path and the cylinders rotatably oscillate relative to the fixed internal cylindrical bearing to control porting for pump and motor operation. Capacity is controlled by a control ring adjustably rotated about the power shaft axis and connected by cranks to the spider to control the angular position of cylinder oscillating movement relative to the position of the ports in the cylindrical bearing to control the porting to vary capacity between zero and full capacity. In a fluid pump or motor, inlet and outlet manifolds and ports provide feed to and discharge from the cylinders. In a compressor there is a feed manifold and discharge through a check valve through the interior of the housing to the outlet.

United States Patent Hause et al.

[ Dec. 11, 1973 PUMPS AND MOTORS [75] Inventors: Gilbert K. Hause, Bloomfield Hills;

William L. Kohler, Detroit, both of Mich.

[73] Assignee: General Motors Corporation,

Detroit, Mich.

[22] Filed: Mar. 24, 1972 [21] Appl. No.: 237,782

[52] U.S. Cl 91/479, 91/494, 417/273, 91/497 [51] Int. Cl. F01b 13/06 [58] Field of Search 91/479, 490, 493, 91/496, 497; 417/269, 467

[56] References Cited UNITED STATES PATENTS 3,211,107 10/1965 Bush 91/479 3,274,946 9/1966 Simmons 91/490 3,695,146 4/1970 Orshansky, Jr. 91/478 1,547,409 7/1925 Cacaud 91/479 1,508,937 9/1924 Pocock et a1... 91/393 3,058,429 10/1962 Rocheville 91/493 3,320,902 5/1967 Paschke 417/269 1,185,955 6/1916 Sundh 91/479 Primary ExaminerWilliam L. Freeh Attorney-W. E. Finken et al.

machine for use as a fluid pump or motor having a drive or driven power shaft rotatably mounted in a housing and having an eccentric and crank mechanism supporting a spider for orbiting movement. The spider has a plurality of radial arms each having fixed on the radial outer end a spherical piston fitting in a cylindrical cylinder. Each piston is coaxially aligned with the radius of its spider arm. The cylinder has a transverse cylindrical base in bearing engagement with a fixed internal cylindrical bearing surface coaxial with the shaft. A manifold in the housing is connected by ports in the internal cylindrical bearing which cooperate with ports in the cylinder base so that during rotation of the power shaft the pistons orbit in a circular path and the cylinders rotatably oscillate relative to the fixed internal cylindrical bearing to control porting for pump and motor operation. Capacity is controlled by a control ring adjustably rotated about the power shaft axis and connected by cranks to the spider to control the angular position of cylinder oscillating movement relative to the position of the ports in the cylindrical bearing to control the porting to vary capacity between zero and full capacity. In a fluid pump or motor, inlet and outlet manifolds and ports provide feed to and discharge from the cylinders. In a compressor there is a feed manifold and discharge through a check valve through the interior of the housing to the outlet.

14 Claims, 13 Drawing Figures PAIENIEU 11975 3,777. 622

saw 2 ur 4 PATENIEBBEBI 1 I975 saw u an;

PUMPS AND MOTORS This invention relates to fluid pressure machines and particularly to a variable capacity orbiting piston and oscillating port controlling cylinder type, of fluid pressure machine.

The fluid pressure machine, a pump or motor, according to this invention, has a power shaft rotatably mounted in a housing and having an eccentric. A spider is mounted on the eccentric for eccentric bodily movement and oscillatory rotation and has a plurality of radial arms, each having fixed on the radial outer end, a sperical piston. The spherical piston fits in a cylindrical cylinder having a cylindrical bearing base portion supported on an internal cylindrical hearing or bearing ring fixed to the housing. The spider movement is controlled by a plurality of cranks connected to a control ring fixed for each degree of capacity. Thus, during rotation of the power shaft, the spider will move in an orbit around the machine axis and the pistons will move in an orbit controlled by the crank mechanism connected to the control ring which is rotatably adjustable for varying the capacity of the machine. The orbiting movement of the pistons causes the pistons to reciprocate in the cylinders and the cylinders to rotatably oscillate relative to the fixed internal cylindrical bearing and control the porting in the internal cylindrical bearing and cylinder base for controlling the transfer of fluid through the machine and thus machine capacity. In this type of construction the high speed power shaft is supported directly in the housing by conventional small bearings and the high speed eccentric cam has a small diameter, since a large diameter for porting is not required. The cylinders, or cups, merely have a small oscillatory movement relative to the internal cylindrical bearing and do not rotate at high speed and thus the high centrifugal load normally found in rotary machines of this character is eliminated. The reciprocating movement of the piston in the cylinder causes the cylinder to move in an oscillatory path on the fixed bearing ring and this movement controls the portion for the pump or motor operation.

These and other features of the invention will be more apparent from the following description and drawings.

FIG. 1 is an elevation view of the fluid pressure machine functioning as a pump with parts in section to show details.

FIG. 2 is a partial view of a piston, cylinder and bearing ring to show the full range of movement of the inlet or suction porting for unloaded or zero capacity operation.

FIG. 3 is a partial view of a piston, cylinder and bearing ring to show the full range of movement of the out let or pressure ports for unloaded or zero capacity operation.

FIG. 4 is a partial view ofa piston, a cylinder and the internal cylindrical bearing ring showing the full range of movement of the inlet or suction ports for full stroke or capacity operation.

FIG. 5 is a partial view of a piston, a cylinder and the internal bearing ring showing the full range of movement of the outlet or pressure ports for full stroke or capacity operation. I

FIG. 6 is a sectional view of FIG. I onthe line 6'6.

FIG. 7 is a partial sectional view of FIG. 1 on the line 7-7 showing the manifold.

FIG. 8 is a developed view showing the ports on the cylinder base and bearing ring.

FIG. 9 is a partial section of FIG. 6 on the line 9-9 showing the displacement control linkage.

FIG. 10 is an end sectional view with parts in section to show details of a modified fluid pressure machine of the compressor type.

FIG. Ill is a partial section of FIG. 10 on the line llll. showing the ports and valve.

FIG. 12 is a sectional view of FIG. 10 on the line Ill-12.

FIG. 13 is a partial sectional view of FIG. 12 on the line 13-l3 showing the displacement control linkage.

The fluid pressure orbiting piston oscillating cylinder machine illustrated in FIGS. 1 to 9 is especially suited for use as a hydrostatic pump or motor. Referring particularly to FIG. 6, a power connector 10 is suitably splined to a power shaft 11, which in a pump is the input or drive shaft and in a motor is the output or driven shaft, has a pair of spaced coaxial bearing portions 12 and I3 rotatably supported respectively in needle bearings l4 and I5 supported in the bearing support portions 16 and 17 of the housing 18 for rotation about shaft or machine axis 19. The shaft 11 between the bearing portions l2 and 13 has on eccentric axis 20, a small cylindrical eccentric portion 21 located centrally between the bearings. The housing 18 has an outer peripheral shell 22 having side plate 23 permanently secured, as by welding, to one side of the shell 22 and a removable cover plate 24 secured by suitable fastening screws 26 to the other side of the shell 22. The bearing support member 17 fits in the central aperture of side plate 23 and is sealed thereto by seal 27 and secured therein by suitable bolts 28. The bearing sup port member 16 similarly fits within the central aperture in housing cover plate 24 and is sealed thereto by seal 29 and secured by screw fasteners 31. It will be noted that the bearing support 17 closes the housing at the free end of shaft 11 and that the connector end of shaft Ill is suitably sealed by a seal 32 between the bearing support portion 16 and the connector member 10 of shaft llll so the housing 18 completely encloses the pumping mechanism.

The central eccentric 21 provides a cylindrical hearing surface, centered on eccentric axis 20, eccentric to the axis 19 of the shaft 11 and the machine axis for the needle bearing 32 which tits in a central cylindrical aperture 33 of the spider 34 which has a central annular portion 35 and a plurality of radially extending arms 36' each terminating-at their outer radial ends in a piston portion 37 coaxial with the radial axis of the arms and having spherical portion 38 contacting the inner cylindrical wall 39 of the cylinder structure 41.

As shown best in FIG. 1, there are 7 pistons, each with a cylinder, but it will be appreciated that the number of pistons and cylinders may be varied to suit design needs. The pistons are equally annularly spaced and located the same radial distance from the center or axis of the spider which, when mounted on the eccentric, is also the center or axis 20 of the eccentric displaced an eccentric distance from the shaft axis.

Each cylinder 41 has a cylindrical portion 40 fitting over the piston and a base portion 42 which has a cylindrical bearing surface 43 perpendicularly transverse to the cylinder axis and fitting the internal bearing surface 44 of bearing ring 45 which is supported on, and secured by, the manifold structure 46, secured within the housing 18.

The manifold structure 46, as best shown in FIGS. 6 and 7, has an outer manifold member 47 and an inner annular member 48, each having a matching central long annular groove to provide the large high pressure or outlet annular passage 51 and on each side thereof two narrow annular grooves to provide two annular low pressure suction or inlet passages 52 and 53. The outer manifold member 47 is fixed to the housing by suitable fasteners, i.e., screws 49. The bearing ring 45 is fixed to the inner manifold member 48 which is fixed to the outer manifold member 47 by suitable fasteners. The parting line between the outer manifold member 47 and the inner manifold portion 48 has suitable annular seals 54 on each side of the annular manifold passages to prevent leakage. There are similar seals 55 between the inner manifold member 48 and the bearing ring 45. At each cylinder station the annular outlet manifold passage 51 is connected by a port 56 extending through the manifold portion 48 and the annular bearing ring 45. The annular inlet manifold passages 52 and 53 are respectively connected by ports 57 and 58 extending through the manifold portion 48 and the annular bearing ring 45. These ports are shown in the developed view, FIG. 8 of the internal surface of bearing ring 45.

The cylinder 41 has in the cylindrical surface 43 of the base portion 42 an outlet port 61 and inlet ports 62 and 63 all communicating with the pumping chamber 64 within the cylinder and sealed by the piston. The pistons 41 are held in the position shown in contact with the annular bearing ring 45 by fluid pressure in the pumping chamber 64 and in the absence of such pressure by annular spring rings 66, one on each side of the spider, and each engaging in a slot 67 in each inner lip of all the cylinders 41.

The inlet port fitting 68, FIG. 7, is suitably secured and sealed to the shell 22 of the housing and connected by a transfer bushing 69 to the outer manifold member 47 and sealed to both the bushing 68 and manifold 47 and connected by passages 71, 72 to the annular inlet manifold passages 52 and 53, as shown in FIG. 7. The outlet port fitting 74, as shown in FIG. 1 is secured and sealed to the housing by suitable fasteners 75 and a seal. The transfer bushing 76, fitting within the passages 77 in the bushing and passage 78 in theouter manifold member 47, is connected by a suitable passage 79 to the outlet manifold annular passage 51.

The orbiting and displacement control mechanism consists of an annular control ring 81 rotatably mounted concentric with shaft 11 axis 19 on a cylindrical bearing surface 82 on the bearing support member 16 and is retained in axial position by a shoulder and snap ring 83. The control ring 81 has a triangular external shape to provide three ears 84, each having an aperture 85 to receive a pin 86 extending from one side of the central portion 93 of crank member 87 which also has an oppositely extending pin 88 fitting into an aperture 89 in an ear 91 formed on the spider 34. The central portion 93 of the cranks 87 fits between the control ring 81 and the ears 91 to position it axially. These cranks 87 have the same eccentric distance as the main eccentric distance between shaft axis 19 and eccentric axis 20. The control ring 81, as shown in FIGS. 6 and 9, has a pair of axially extending ears 92 with the ball end 94a of control lever 94 therebetween. The control lever 94 is suitably keyed to the control shaft 95 extending through a seal in aperture 96 in the housing and connected to a suitable control lever 97. When the control lever is moved to control capacity, the lever rotates the control ring 81 within the limits defined by the pins 98 and 99 fixed in the housing portion 24 and engaging ears 92 to limit movement.

The eccentric flywheel 101 has a ring portion 102 fitting on the bearing portion 13 and is secured by a suitable screw 103 to the side of the eccentric portion 21 and an eccentric weight portion 104 to balance the eccentric and the spider on the main shaft and about the main shaft axis. The eccentric out of balance weight is reduced by apertures 106.

The operation of this fluid machine as a pump is described particularly in conjunction with FIGS. 1 to 5. When the pump input shaft 11 is driven in a clockwise direction, viewed from the shaft end of the pump and as indicated by the arrow A in FIG. 1, the eccentric center, or eccentric axis 20, rotates clockwise, arrow A of FIG. 1, about the shaft or machine axis 19. For convenience in describing the operation, we have indicated the position shown in FIG. 1 with the eccentric center 20 below shaft axis 19 as the zero degree angular position. The angular position of the eccentric center about axis 19 on moving from the zero degree position clockwise and 270 is indicated by the dotted radii and the legends 0, 90, 180 and 270 indicating these positions of the eccentric center about axis 19. Only the shaft 11 and the eccentric 21 thereon is rotatably driven from a suitable source of power and thus has continuous rotation. The spider, due to the fact that its movement at the center is in the eccentric path and radially outward of the center is controlled by orbiting means, the cranks 87 connected to the spider and by the ring 81 to the housing, has a limited path of bodily orbiting movement, a combination of reciprocating and transverse oscillating movement. The orbiting means thus controls orbiting movement of the spider and the pistons fixed thereon in relation to the fixed support housing and transmits reaction forces of excursion movement E, FIG. 4. Since the crank throw or the distance between the pins 86 and 88 is the same as the ec centric distance, the distance between shaft axis 19 and eccentric axis 20, all positions of the spider piston center line during orbiting movement are parallel to each other. The full capacity positions of the pistons are illustrated in FIGS. 1, 4 and 5. The center line of piston P is on the vertical line B or radius through both the shaft and eccentric centers 19 and 20 in the bottom position at 0 and as shown at the top 180 position in FIG. 1. As indicated in FIG. 4 the piston center line is on center line B for the 0 and 180 positions, and on center line C in the 90 position shown in solid lines and on center line D in the 270 position shown in dotted lines which are all parallel. Thus, as the eccentric center 20 moves from the 0 position, FIG. 1, through the 90 position, solid lines in FIGS. 4 and 5, to the 180 position, piston P moves from bottom dead center as shown in solid lines (FIG. 1) to the top dead center position. With continued eccentric rotation from the 180 position through the 270 position, dotted lines in FIGS- 4 and 5, to the 0 position, the piston returns to the bottom dead center position shown. Thus, the piston moves in a circular orbiting path providing a combination of both-radial reciprocating movement and to and fro or transverse bodily movement from the central position at the 90 and 180 position, illustrated in FIG.

1 at the 180 position. The spherical piston fits in the cylinder and causes excursion or rotary oscillating movement of the cylinder on the cylindrical bearing ring concentric with shaft axis 19. Thus the spider and pistons and cylinders do not continuously rotate. Since the cylinder bore axis is radial to the cylindrical bearing base of the cylinder it is also radial to the bearing ring. Since the spherical piston seals the cylinder in a plane perpendicular to the cylinder axis, the summation vector of force transmitted is on the cylinder axis radial to the bearing ring and thus through the shaft axis 19. Accordingly, the force delivered by, as in a pump or to, as in a motor, the eccentric at axis 19 has a reaction grounded by cranks 87. At the 90 position, the piston 37 and the cylinder 41 which is carried with it is at the left as shown in solid lines in FIG. 4 and with 180 of movement to the 270 position moves to the opposite side of center to the dotted line position through an excursion distance E Thus in eccentric rotary positions 0, 90, 180 and 270 the piston axis is respectively in parallel positions B, C, B and D and the cylinder axis is respectively in radial positions B, C, B and D. Note that piston axis B and cylinder axis B are identical. This excursion movement of the piston and cylinder 41 relative to the fixed bearing ring 45 controls the valve porting. With the eccentric in the 0 position shown in FIG. 1, and rotating clockwise, arrow A, the pressure port 56 in ring 45 is just opening to the pressure port 61 in the cylinder head and remains opened as the cylinder moves to the full line position C, FIG. 5, at 90 and closes at the 180 position B with the cylinder in the top dead center position, illustrated in FIG. 1 by the dotted line cylinder Pl. As the cam continues to rotate from the 180 position through the 270 position D and then to the 0 position, the pressure port 56 remains closed since the pressure port 61 in the cylinder is to the right of it, as shown in dotted lines in FIG. 5. The suction ports have an opposite cycle, as shown in FIG. 4 and with the cam in the 0 position the suction port 57 is just closed and remains closed as the eccentric moves through the 90 position C' (solid lines) to the 180 position. On continued movement of the cam past the 180 position, suction port 57 opens to the port 62 and remains opened on continued rotation through the 270 position D (dotted lines) to the 0 position where it closes.

The capacity of this pump may be varied by rotating the control ring 81 to change the position of the cranks relative to the housing and thus rotatably or angularly varying the position of the excursion or rotary oscillating movement of the cylinder relative to the ports in the bearing ring 45. In the configuration shown, when the control ring is in the full capacity position, as shown in FIGS. 1, 4 and 5, the overlap period when both pressure and suction ports are closed is only at the 0 and 180 position and the pressure and suction ports are each open for substantially 180 of eccentric rotation. When the control ring is rotated clockwise like arrow A, the overlap is increased to the same degree so that the port openings occur in prgressively reduced portions of the excursion movement of the cylinders or during progressively reduced portions of the angular movement of the cam center 20 about axis 19. The port opening portion of angular movement is centered about the 90 and 270 positions.

FIGS. 2 and 3 illustrate such stroke adjustment to the zero capacity, or fully unloaded position. The axis of piston 37 and cylinder 41 in the 0 and 180 positions, cylinder axis B, is thus displaced or rotated clockwise as shown in FIGS. 2 and 3. The cylinder axis C for the position and D for the 270 position, are similarly displaced but remain equally spaced to the 0 and position axis B. The piston axis has similar parallel positions during excursion movement. The piston 34 and cylinder 41, during excursion movement between the solid line 90 position and dotted line 270 position, have the same excursion movement E, however, as shown in FIG. 2, the suction port 57 in the ring 45 is always open to the suction port 62 in the cylinder 41. The pressure port 56 as shown in FIG. 3, is always closed with respect to the pressure port 61 in the cylin' der 41. Thus, there is no delivery of pressure fluid and with the suction on low pressure port 57 always opened throughout 360 of movement of the cam 21, there is no pumping action. The other pistons and cylinders function in the same way.

Each of the pistons, cylinders and porting means on the cylinder base and bearing ring consecutively function in the same way to provide when operating as a pump continuous delivery of fluid from the inlet port 68 to supply fluid under pressure to the outlet port 74. When pressure is supplied to the inlet port the machine will similarly function as a motor.

The fluid pressure orbiting piston and oscillating cylinder machine illustrated in FIGS. 10 to 13 is particularly suited for use as a compressor and has an input pulley 111 secured by suitable fastener 1 l2 and splines 113 to the input or power shaft 114. Shaft 114 has an inner end eccentric portion 116 with a cylindrical bearing surface 117 for the needle bearing 118 fitted within the central bore 119 of the oscillating spider 121. The shaft is supported within a cylindrical bearing support sleeve portion 122 which extends inboard and outboard of the sidewall 123 of the housing 124. The shaft 114 has an inboard cylindrical bearing portion 126 cooperating with the needle bearing 127secured in the inboard portion 128 of the sleeve 122. Adjacent to this bearing a reduced diameter sealing portion 131 of the sleeve 122 cooperates with an O ring 132 for a first seal. The outboard end of the shaft 114 is supported by a roller bearing 133 fitted in the outboard portion 134 sleeve 122. Between the shaft bearings, there is a spring biased shaft seal structure 136 which has a portion 137 secured and sealed within the sleeve 122. The rotating seal portion 138 has an O ring seal 139 and biasing spring 141 all rotating with the shaft and held by the spring in engagement with an abutment on the shaft and the rotating face seal 142 which engages fixed seal 137.

The spider 121 has an inner ring portion 146, a plurality of hollow lightweight radial arms 147 which are axially offset to reduce the axial length of the machine. Each of the arms 147 has an annular lip flange portion 148 which receives the piston member 149 which has a closure plate portion 151 and an annular flange portion 152 having a spherical piston surface 153. This piston member 149 is secured by snap ring 154 to the arm 147. The sperical piston surface 153 has a sealing fit in the cylinder bore 156 of the cylindrical portion 157 of the cylinder 158. Cylinder 158 alsohas a base portion 159 having a transverse cylindrical bearing surface 161 in bearing engagement with the inner cylindrical hearing surface 162 of the bearing ring 163 which is fixed within the cylindrical wall portion 164 of the cover portion 165 of the housing 124. The suction or inlet pipe 166 is connected through cylindrical wall 164 to an annular manifold passage 167 between the housing cylindrical wall 164 and in a recess in the bearing ring 163. Seals 168 on opposite sides of this annular passage seal the passage. The lower portion 171 of housing 164 is enlarged to provide a storage chamber 172. The housing portion 165 and the housing portion 124 at their meeting edge have flanges 173 engaged by a U-shaped loop clamp 174 to secure the parts together.

At each pumping station for each cylinder the manifold is connected by a passage 176 extending from the manifold to the bearing surface 162 of the bearing ring 163. The cylinder base 159 has a closure portion 177 closing the port 176 at times and at other times the port 176 connects to the cylinder bore 156 which, as pointed out above, is opened at both ends except for closure by the piston. The piston cover portion 151 has two outlet ports 181, as best shown in FIG. 11, both covered by the enlarged end 182 of the leaf spring valve 183. A rigid guide plate 184 is located at the back of the valve spring 183 and both this plate and the valve spring are secured by suitable fasteners 186 to the underside of the piston head, or cover. When outlet pressure reaches the desired value, leaf spring valve 183 is deflected permitting flow from the pumping chamber through ports 181 to the interior of the housing. The backing member 184 limits and defines this flexing movement of the leaf spring valve 183 for a long life spring valve. The interior housing chamber 188 receiving the pumped fluid has an outlet passage 189 to supply fluid.

A pair of double spring rings 191 engage the side flange portion 192 of the base 159 of the cylinders 158 to hold the cylinders against the bearing ring 163 when the pressure is not present to do so.

The capacity control mechanism has a control ring 196 rotatably mounted on an external bearing surface 197 upon the housing support sleeve portion 122. A plurality of crank members 198 have one pin portion 199 extending into and rotatably mounted in bearing bores 201 in the spider and another crank pin 202 extending into and rotatably mounted in bearing bores 203 in ears 204 of the control ring 196. Between a pair of ears 204 there is a stop cam 206 having a pair of opposed shoulders 207 and 208 cooperating with a pin 209 fixed in the wall 123 to limit rotary movement of the control ring 196. The control ring 196 also has an arm 211 having a ball socket 212 to receive the ball end 213 of the lever 214 which is fixed in a transverse bore 216 in the control shaft 217 and thus perpendicular to this shaft. The control shaft is rotatably mounted and sealed in a radial bore 218 in the wall portion 123 of the housing and extends radially outside the housing where is has secured thereto an actuating lever 219 or capacity control lever 219.

A space around shaft 114 in sleeve 122 between the seals 132 and 136 is connected by a port 221, a passage 222 through the control shaft 217, a passage 224 in the manifold 163 and to the inlet annular chamber 167 in order to connect the space between the bearings to vent the leakage space to the low pressure inlet of the compressor.

In the machine illustrated in FIG. to 13, the eccentric axis 226 is offset the same distance from the machine axis 227 as the throw of the crank 198 so the spider 121 and its pistons has the same oribiting movement as the above described machine, illustrated in FIGS. 1 to 9. As in the machine of FIGS. 1 to 9, in the FIGS. 10 to 13 machine, the bearing ring 163 is similarly centered about the machine axis, the cranks 198 are pivoted by pin portions 198 in openings 201 in the spider concentric with the eccentric axis 226, the other crank pin 202 is pivoted in openings 203 concentric with the machine axis 22 and the cylinder bore axis is radial relative to the cylindrical cylinder base and bearing ring internal bearing surface. When this machine is driven clockwise, as viewed when facing the shaft and from the other end of the machine counter-clockwise as indicated by the arrow H, in FIG. 10, the suction ports 176-175 will be similarly closed as the eccentric rotates about the shaft axis from the 0 position through the position to the position which is the pressure stroke during which the piston moves from bottom to top dead center, the position shown in FIG. 10. The suction ports 176-175 then will open as the eccentric continues to rotate past the 180 position through the 270 position to the 0 position providing the suction stroke as the piston moves from top to bottom dead center. The pressure stroke occurs during the time when the inlet port 176 is closed by the base portion 177 of the cylinder and will cause pressure developed in the contracting operating chamber to open the check valve 183 to deliver fluid to the outlet. The check valve 183 will be closed by the outlet pressure during the suction stroke. In FIG. 10 the piston head 151 is shown at the top dead center of stroke, or the 180 position, having just delivered fluid through the valve 183 to chamber 188 in the housing 124. During continued rotation from the 180 position through the 270 position to the diametrically opposite 0 position of the cam center axis 226 about the shaft axis or center 227 in the direction of arrow H, the suction port 176 remains opened for the suction stroke. At the 0 position, the piston head 151 will be in the bottom dead center position and then on continued rotation of the cam from the 0 position through the 90 position to the 180 position, the piston will move from bottom dead center to the top dead center position illustrated in FIG. 10 providing the discharge or pressure stroke forcing compressed fluid through the outlet valve 183.

Movement of the control ring 196 in the same direction as the .direction of rotation H will, as in the above modification shown in FIGS. 1 to 9, move the oscillation center so that the inlet or suction port 176 is opened for a longer period of time, thus reducing the pressure a discharge stroke portion and gradually reducing the capacity of the machine or the output of the device as a pump. In the unloaded or zero capacity position of the capacity control ring 196, the suction port 176 remains open at all times or through 260 of movement of the eccentric so that there is no pumping action.

It will be appreciated that the above disclosed specific embodiments are subject to modification in accordance the the teachings of this invention.

It is claimed:

1. In a hydraulic machine; a support housing including a bearing ring fixed on said housing having an internal bearing surface circular about a shaft axis; a shaft mounted on said housing for rotation about the shaft axis and having an eccentric bearing portion rotating with said shaft and having an eccentric axis rotating about said shaft axis during rotation of said shaft; a spider having a central portion mounted on said eccentric bearing for rotation of said shaft eccentric bearing portion relative to said spider and having a plurality of arms rigidly fixed to the central portion and extending outwardly and each arm having a sperical piston and each piston being located at a radially offset piston station; orbiting means connected to said housing and said spider to provide a path of orbiting movement, a combination of a limited extent of radially reciprocating and rotary oscillating movement, of each of said pistons in its piston station relative to said bearing ring in coordination with movement of said central portion of said spider and rotation of said eccentric bearing portion; a cylinder on each piston having a bearing base slidably mounted on said internal bearing surface of said bearing ring and a cylindrical bore extending radially inwardly of said internal bearing surface and fitting on the sperical piston providing a variable volume chamber therebetween varying with said radially reciprocating movement of said piston and providing rotary oscillating movement of said cylinder on said internal bearing surface in response to rotary oscillating movement of said piston; and fluid supply and control means on said cylinder and said housing for providing and controlling flow of fluid to and flow of fluid from said chamber in response to said rotary oscillating movement of said cylinder in phase relation to said radially reciprocating movement of said piston.

2. The invention defined in claim 1 and means to control said orbiting means to rotatably adjustably displace said path of orbiting movement to cause rotary adjustment of said rotary oscillating movement of said cylinder relative to said bearing ring to change the time of opening and closing of said ports relative to radial reciprocating movement of said pistons to vary machine capacity.

3. The invention defined in claim 1 and said fluid supply and control means including a port for each cylinder in said bearing ring and a port in each cylinder base controlled by said rotary oscillating movement of said cylinder to open and close fluid communication between said ports for controlling a flow.

4. The invention defined in claim 1 and means to control said orbiting means to adjust said path of orbiting movement to cause said rotary oscillating move ment of said cylinder to change to vary the control of said fluid supply and control means to vary machine capacity.

5. In a hydraulic machine; a support housing including a bearing ring fixed on said housing having an internal bearing surface circular about a shaft axis; a shaft mounted on said housing for rotation about the shaft axis and having an eccentric bearing portion rotating with said shaft and having an eccentric axis rotating about said shaft axis during rotation of said shaft; a spider having a central portion mounted on said eccentric bearing for rotation of said shaft eccentric bearing portion relative to said spider and having a plurality of arms rigidly fixed to the central portion and extending outwardly and each arm having a spherical piston and each piston being located in a radially offset piston station; orbiting means connected to said housing and said spider to provide orbiting movement, a combination of radial reciprocating and rotary oscillating movement, of each of said pistons in its piston station relative to said bearing ring in coordination with movement of said central portion of said spider and rotation of said eccentric bearing portion; a cylinder on each piston having a bearing base slidably mounted on said internal bearing surface of said bearing ring and a cylindrical bore extending radially inwardly of said internal bearing surface and fitting on the spherical piston providing a variable volume chamber therebetween varying with said radial reciprocating movement of said piston and providing rotary oscillating movementof said cylinder on said internal bearing surface in response to orbiting movement of said piston; fluid supply and return means; port means, including a port in said internal bearing surface of said bearing ring and a port in said cylinder base selectively aligned for open fluid communication and misaligned to close to block fluid communication responsive to rotary oscillatory movement of said cylinder, for controlling flow of fluid between said fluid supply and return means and said chamber in phase with said radial reciprocation of said piston.

6. The invention defined in claim 5 and said orbiting means having adjustment means to rotatably displace the orbiting movement of said piston to rotatably displace the rotary oscillating movement of said cylinder to control said port means to vary the period in which said ports are aligned for open fluid communication and misaligned to block fluid communication during each revolution of said shaft to vary machine capacity.

7. The invention defined in claim 6 and said adjustment means being rotatable control ring mounting said orbiting means on said housing and being rotatable to vary machine capacity.

8. In a hydraulic machine; a support housing; a shaft mounted on said housing for rotation about a shaft axis and having an eccentric bearing portion rotatable with said shaft having an eccentric axis rotating about said shaft axis during rotation of said shaft; a spider having a central portion having an aperture mounted on said eccentric bearing for rotation of said shaft eccentric bearing portion in said aperture and having a plurality of arms extending outwardly and. each arm having a spherical piston equally spaced from said eccentric axis and each piston being located in a radially offset piston station; orbiting means connected to said housing and said spider to provide orbiting movement, a combination of radial reciprocating movement and rotary oscillating movement, of each of said pistons in its piston station relative to said housing in coordination with eccentric movement of said central portion of said spider and rotation of said rotating eccentric bearing portion; a bearing ring fixed on said housing having an internal cylindrical bearing surface concentric with said shaft axis; a cylinder on each piston having a cylindrical bearing base fitting said internal cylindrical bearing surface of said bearing ring for sliding rotary movement and a cylindrical bore extending radially inwardly of said internal cylindrical bearing surface and fitting on the spherical piston providing a variable volume chamber therebetween varying with said radial reciprocating movement of said piston and providing rotary oscillating movement of said cylinder on said internal cylindrical bearing surface in response to rotary oscillating movement of said piston; fluid supply and return means; port means, including a port in said internal surface of said bearing ring and a port in said cylinder base selectively aligned for open fluid communication and misaligned to close to block fluid communication between said fluid supply responsive to oscillatory movement of said cylinder, for controlling flow of fluid between said fluid supply and return means and said chamber in phase with said radial reciprocation of said piston.

9. In a hydraulic machine; a support housing; a shaft mounted on said housing for rotation about a shaft axis and having an eccentric bearing portion rotatable with said shaft and having an eccentric axis rotating about said shaft axis during rotation of said shaft; a spider having a central portion having an aperture mounted on said eccentric bearing for rotation of said shaft eccentric bearing portion in said aperture and having a plurality of arms rigidly fixed to the central portion and extending radially outwardly from said eccentric axis and each arm having a spherical piston equally spaced from said eccentric axis and each piston being located in a radially offset piston station; a crank assembly having crank with a shaft at one end rotatably connected to said housing and a shaft at the other end rotatably connected to said spider to provide and control orbiting movement, a combination of radially reciprocating and rotary oscillating movement, of each of said pistons in its piston station relative to said housing in coordination with the eccentric movement of said central portion of said spider by said eccentric bearing portion; a bearing ring fixed on said housing having an internal cylindrical bearing surface concentric with said shaft axis; a cylinder on each piston having a cylindrical bearing base fitting said internal cylindrical bearing surface of said bearing ring for rotary sliding movement and a cylinder bore extending radially inwardly of said internal cylindrical bearing surface and fitting on the spherical piston providing a variable volume chamber therebetween varying with said radial reciprocation of said piston and providing rotary oscillating movement of said cylinder on said internal cylindrical bearing surface in response to said orbiting movement of said piston; fluid pressure supply and return means; port means, including a port in said inner bearing surface of said bearing ring and a port in said cylinder base selectively aligned for open fluid communication and misaligned to close to block fluid communication responsive to rotary oscillatory movement of said cylinder, for controlling flow between said fluid supply and return means and said chamber in phase with said radial reciprocation of said piston.

10. The invention defined in claim 9 and said crank having a throw distance equal to the eccentric distance between said shaft axis and said eccentric axis.

11. The invention defined in claim 9 and a port through said piston; a oneway leaf spring valve controlling said port in said piston.

12. The invention defined in claim 9 and said bearing ring having an inlet and outlet port for each cylinder and an inlet and outlet port in each cylinder base.

13. The invention defined in claim 9 and said crank assembly including means to rotatably displace the orbiting movement of said piston to rotatably displace the oscillating movement of said cylinder to control said port means to vary the period said ports are aligned for open fluid communication and misaligned to block fluid communication during each revolution of said shaft to vary machine capacity.

14. The invention defined in claim 13 and a rotatable control mounting said shaft at one end of said crank on said housing and being adjustably rotatable to vary machine capacity.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent: No. 3" I 111 522 Dated December 1l, 1973 Inventofls) "Gilbert K. Hause et a1 It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

lt n the specification, column 1, line 41 "portion" should be .1

n porting column 4, line 67,"90" should be'-- 0 column 5, line 60, "prgressivel should be progressively column 8, line 54, numeral "260 should be 360 column 8, m line 59, "the" first occurrence, should be with In the claims,- column 10, claim 7, line 28, insert a before "rotatable". to n Signed and sealed this lL th day of May 19m.

-(SEAL) Attest; r l EDWARD I-l.FLETCl-IER,JR. v n l o 0; MARSHALL-ZDANN AttsstingOfficer Commissioner of- Patents 

1. In a hydraulic machine; a support housing including a bearing ring fixed on said housing having an internal bearing surface circular about a shaft axis; a shaft mounted on said housing for rotation about the shaft axis and having an eccentric bearing portion rotating with said shaft and having an eccentric axis rotating about said shaft axis during rotation of said shaft; a spider having a central portion mounted on said eccentric bearing for rotation of said shaft eccentric bearing portion relative to said spider and having a plurality of arms rigidly fixed to the central portion and extending outwardly and each arm having a sperical piston and each piston being located at a radially offset piston station; orbiting means connected to said housing and said spider to provide a path of orbiting movement, a combination of a limited extent of radially reciprocating and rotary oscillating movement, of each of said pistons in its piston station relative to said bearing ring in coordination with movement of said central portion of said spider and rotation of said eccentric bearing portion; a cylinder on each piston having a bearing base slidably mOunted on said internal bearing surface of said bearing ring and a cylindrical bore extending radially inwardly of said internal bearing surface and fitting on the sperical piston providing a variable volume chamber therebetween varying with said radially reciprocating movement of said piston and providing rotary oscillating movement of said cylinder on said internal bearing surface in response to rotary oscillating movement of said piston; and fluid supply and control means on said cylinder and said housing for providing and controlling flow of fluid to and flow of fluid from said chamber in response to said rotary oscillating movement of said cylinder in phase relation to said radially reciprocating movement of said piston.
 2. The invention defined in claim 1 and means to control said orbiting means to rotatably adjustably displace said path of orbiting movement to cause rotary adjustment of said rotary oscillating movement of said cylinder relative to said bearing ring to change the time of opening and closing of said ports relative to radial reciprocating movement of said pistons to vary machine capacity.
 3. The invention defined in claim 1 and said fluid supply and control means including a port for each cylinder in said bearing ring and a port in each cylinder base controlled by said rotary oscillating movement of said cylinder to open and close fluid communication between said ports for controlling a flow.
 4. The invention defined in claim 1 and means to control said orbiting means to adjust said path of orbiting movement to cause said rotary oscillating movement of said cylinder to change to vary the control of said fluid supply and control means to vary machine capacity.
 5. In a hydraulic machine; a support housing including a bearing ring fixed on said housing having an internal bearing surface circular about a shaft axis; a shaft mounted on said housing for rotation about the shaft axis and having an eccentric bearing portion rotating with said shaft and having an eccentric axis rotating about said shaft axis during rotation of said shaft; a spider having a central portion mounted on said eccentric bearing for rotation of said shaft eccentric bearing portion relative to said spider and having a plurality of arms rigidly fixed to the central portion and extending outwardly and each arm having a spherical piston and each piston being located in a radially offset piston station; orbiting means connected to said housing and said spider to provide orbiting movement, a combination of radial reciprocating and rotary oscillating movement, of each of said pistons in its piston station relative to said bearing ring in coordination with movement of said central portion of said spider and rotation of said eccentric bearing portion; a cylinder on each piston having a bearing base slidably mounted on said internal bearing surface of said bearing ring and a cylindrical bore extending radially inwardly of said internal bearing surface and fitting on the spherical piston providing a variable volume chamber therebetween varying with said radial reciprocating movement of said piston and providing rotary oscillating movement of said cylinder on said internal bearing surface in response to orbiting movement of said piston; fluid supply and return means; port means, including a port in said internal bearing surface of said bearing ring and a port in said cylinder base selectively aligned for open fluid communication and misaligned to close to block fluid communication responsive to rotary oscillatory movement of said cylinder, for controlling flow of fluid between said fluid supply and return means and said chamber in phase with said radial reciprocation of said piston.
 6. The invention defined in claim 5 and said orbiting means having adjustment means to rotatably displace the orbiting movement of said piston to rotatably displace the rotary oscillating movement of said cylinder to control said port means to vary the period in which said ports are aligned for open fluid communication and misaligned to block fluid communication during each revolution of said shaft to vary machine capacity.
 7. The invention defined in claim 6 and said adjustment means being rotatable control ring mounting said orbiting means on said housing and being rotatable to vary machine capacity.
 8. In a hydraulic machine; a support housing; a shaft mounted on said housing for rotation about a shaft axis and having an eccentric bearing portion rotatable with said shaft having an eccentric axis rotating about said shaft axis during rotation of said shaft; a spider having a central portion having an aperture mounted on said eccentric bearing for rotation of said shaft eccentric bearing portion in said aperture and having a plurality of arms extending outwardly and each arm having a spherical piston equally spaced from said eccentric axis and each piston being located in a radially offset piston station; orbiting means connected to said housing and said spider to provide orbiting movement, a combination of radial reciprocating movement and rotary oscillating movement, of each of said pistons in its piston station relative to said housing in coordination with eccentric movement of said central portion of said spider and rotation of said rotating eccentric bearing portion; a bearing ring fixed on said housing having an internal cylindrical bearing surface concentric with said shaft axis; a cylinder on each piston having a cylindrical bearing base fitting said internal cylindrical bearing surface of said bearing ring for sliding rotary movement and a cylindrical bore extending radially inwardly of said internal cylindrical bearing surface and fitting on the spherical piston providing a variable volume chamber therebetween varying with said radial reciprocating movement of said piston and providing rotary oscillating movement of said cylinder on said internal cylindrical bearing surface in response to rotary oscillating movement of said piston; fluid supply and return means; port means, including a port in said internal surface of said bearing ring and a port in said cylinder base selectively aligned for open fluid communication and misaligned to close to block fluid communication between said fluid supply responsive to oscillatory movement of said cylinder, for controlling flow of fluid between said fluid supply and return means and said chamber in phase with said radial reciprocation of said piston.
 9. In a hydraulic machine; a support housing; a shaft mounted on said housing for rotation about a shaft axis and having an eccentric bearing portion rotatable with said shaft and having an eccentric axis rotating about said shaft axis during rotation of said shaft; a spider having a central portion having an aperture mounted on said eccentric bearing for rotation of said shaft eccentric bearing portion in said aperture and having a plurality of arms rigidly fixed to the central portion and extending radially outwardly from said eccentric axis and each arm having a spherical piston equally spaced from said eccentric axis and each piston being located in a radially offset piston station; a crank assembly having crank with a shaft at one end rotatably connected to said housing and a shaft at the other end rotatably connected to said spider to provide and control orbiting movement, a combination of radially reciprocating and rotary oscillating movement, of each of said pistons in its piston station relative to said housing in coordination with the eccentric movement of said central portion of said spider by said eccentric bearing portion; a bearing ring fixed on said housing having an internal cylindrical bearing surface concentric with said shaft axis; a cylinder on each piston having a cylindrical bearing base fitting said internal cylindrical bearing surface of said bearing ring for rotary sliding movement and a cylinder bore extending radially inwardly of said internal cylindrical bearing surface and fitting on the spherical piston providing a variable volume chAmber therebetween varying with said radial reciprocation of said piston and providing rotary oscillating movement of said cylinder on said internal cylindrical bearing surface in response to said orbiting movement of said piston; fluid pressure supply and return means; port means, including a port in said inner bearing surface of said bearing ring and a port in said cylinder base selectively aligned for open fluid communication and misaligned to close to block fluid communication responsive to rotary oscillatory movement of said cylinder, for controlling flow between said fluid supply and return means and said chamber in phase with said radial reciprocation of said piston.
 10. The invention defined in claim 9 and said crank having a throw distance equal to the eccentric distance between said shaft axis and said eccentric axis.
 11. The invention defined in claim 9 and a port through said piston; a one-way leaf spring valve controlling said port in said piston.
 12. The invention defined in claim 9 and said bearing ring having an inlet and outlet port for each cylinder and an inlet and outlet port in each cylinder base.
 13. The invention defined in claim 9 and said crank assembly including means to rotatably displace the orbiting movement of said piston to rotatably displace the oscillating movement of said cylinder to control said port means to vary the period said ports are aligned for open fluid communication and misaligned to block fluid communication during each revolution of said shaft to vary machine capacity.
 14. The invention defined in claim 13 and a rotatable control mounting said shaft at one end of said crank on said housing and being adjustably rotatable to vary machine capacity. 